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Feb. 1, 1955 c, PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 31,1949 6 Sheets-Sheet l IN VEN TOR. Char [es /7. fal'terfl HTTORNE).

Feb. 1, 1955 c, PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 31,194 9 6 Sheets-Sheet 2 IN VEN TOR. Char/e5 x7, Par/(er Feb. 1, 1955 g,PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 31,1949 6 Sheets-Sheet 3 A67 ma INVENTOR. Charles J]. Par-fie) Feb. 1, 1955c, A PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 51,1949 6 Sheets-Sheet 4 v INVENTOR.

Cid/{es JZ Paw/Tel BY gghgw HTTOAIVEY.

Feb. 1, 1955 Q A. PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 31,1949 6 Sheets-Sheet 5 128 130 175 0 9 INVENTOR.

Cfiarles .19. Parker" HTTORNEY.

Feb. 1, 1955 c, PARKER 2,701,094

REGISTER SHIFT TIMING MECHANISM FOR CALCULATING MACHINES Filed Aug. 51,1949 6 Sheets-Sheet 6 IN VEN TOR. (flax-[es A Rwwfen 177' 7' ORA/E KUnited States Patent REGISTER SHIFT TIMING MECHANISM FOR CALCULATINGMACHINES Charles A. Parker, Knoxville, Tenn., assignor, by mesneassignments, to Burroughs Corporation, a corporation of MichiganAppiication August 31, 1949, Serial No. 113,402

17 Claims. (Cl. 235-60) This invention relates to the art of calculatingmachines. It is concerned in particular with the register mechanism ofsuch machines. Conventional calculating machine practice makes use of aregister which incorporates some form of rack movable between two limitpositions through a definite cycle to rotate register pinions inaccordance with the directional movement of the rack. The pinions arevariously shifted into and from mesh with their racks. Known machinesemploy relatively complicated mechanisms for effecting the shift of theregister pinions at the appropriate time. Such mechanisms entail the useof a large number of separate parts and usually the various parts arelocated at spaced points about the machine assembly.

An object of this invention is to provide a timing mechanism foretfecting shift of the register pinions and which provides a compactunit that contains substantially all necessary elements to accomplishdesired shifting of the register pinions. The unit is relatively smalland occupies but little space and it condenses into one assembly theessential mechanism necessary for timing shifting of the registerpinions.

Another object is to provide means for transmitting actuating energyfrom the main operating member of a calculating machine to the registerpinion shifting means, in which a single compact element in fixedrelation to the operating member furnishes the motive force for aplurality of shift elfecting mechanisms which operate separately and atdifferent times at different locations.

A further object is to provide register pinion shifting mechanisms forcalculating machines having means for freeing from idling movement allparts not necessary to the performance of work when other parts requiredto perform work are being moved to accomplish a shifting of the pinions.

Another object is to provide, in a calculating machine having anoperating member movable through a cycle and a plurality of separatelyacting register pinion shifting mechanisms driven therefrom during itscycle, means for removing from driving actuation by the operating memberall parts of those shifting mechanisms not called upon to perform workwhen any one of the shifting mechanisms is working.

Still another object is to provide timing means for register pinionshifting mechanism in a calculating machine, in which the various shiftsof the pinions into and from mesh with their racks are all controlledfrom a single fixed element on a movable operating member of themachine, in cooperation with a plurality of devices operativeselectively at predetermined points along the path of movement of theoperating member to effect pinion shift in either of two oppositedirections when the operating member element is at those points.

A further object is to provide a driving connection between theoperating member and the register pinion shifting mechanism of acalculating machine, in which oppositely acting linkages form acoupling, with means operative selectively to disengage the couplingwith respect to any linkage whereby to control the direction of pinionshift.

Other objects apparent to persons skilled in the art are incorporated inthe following specification, which is illustrative and not restrictive.

in the accompanying drawings:

Fig. l is an elevation of a timing mechanism assembly constructed inaccordance with this invention, the view being from the right hand sideof the mechanism consid 2,701,094 Patented Feb. 1, 1955 ice ered on thelongitudinal axis running from front to rear of the machine in which themechanism is incorporated;

Fig. 2 is a similar elevation but taken from the left, or opposite, sidewith respect to Fig. 1;

Fig. 3 is an elevation of the structure of Fig. 1 with parts removed andbroken away for clearness of illustration;

Pig. 4 is an elevation from the right hand side of the apparatusillustrating details of the register shift mechanism;

Fig. 5 is a rear view of the assembly of Fig. 1;

Fig. 6 is a front view of the assembly with parts broken away forclearness of detail;

Fig. 7 is a fragmentary elevation illustrating a detail of themechanism;

Fig. 8 is a top plan view of the assembly;

Fig. 9 is a top plan view of a portion of the assembly shown in Fig. 8;

Fig. 10 is a fragmentary elevation illustrating certain details of themechanism;

Fig. 11 is a longitudinal section taken substantially on the line 11-11of Fig. 1 illustrating the position of parts when the apparatus isconditioned for addition or subtraction in the register;

Fig. 12 is a view similar to Fig. 11 but illustrating the position ofthe parts when the apparatus is conditioned for a subtotal operation;

Fig. 13 is also a view similar to Fig. 11 but illustrating the positionor" the parts when the apparatus is conditioned for a total takingoperation; and

Figs. 14 and 15 are illustrations of details of the mechanism.

In the present embodiment of the invention the timing mechanism ismounted on a vertically planar support S that is disposed longitudinallyparallel to the longitudinal axis of the machine in which the mechanismis incorporated. By way of reference, the present mechanism isincorporated in the accounting machine illustrated in the copendingapplication of Charles A. Parker and Clifton K. Rainey, Serial No.99,081, filed June 14, 1949. it is to be understood, however, that thetiming mechanism of this invention is readily adaptable to other typesof calculating machines and the reference is by way of illustration andnot by way of limitation. The support has front and rear leg portions 18and 19, respectively, that are rigidly attached to elements of themachine frame secured to the base B of the machine. The bottom portionof the support between the legs 18 and 19, is cut away to accommodatemovement of an operating member 20. The operating member 20 is driven bysuitable means, not shown, to reciprocate through a full cycle at eachactuation. Its path of reciprocation is be tween the support legs 18 and19 and it operates between forward and rearward limit positions. Therearward limit position of the operating member, as shown in Figs. 1 and2, is its position of rest which it occupies prior to and at theconclusion of a cycling operation.

Energy of the operating member is utilized to shift register pinions inthe register section of the machine in which the apparatus isincorporated. Fig. 4 indicates a portion of the register section of themechanism, which incorporates a set of register pinions 21 adapted forshifting into and from engagement with side bars 22 and 23 which areelements of the racks of the calculating mechanism. In the illustrationof Fig. 4, the toothed bars 22 comprises the addition side of the rackswhile the bars 23 comprise the subtraction side. This arrangement may bevaried as desired and is by way of illustration only. Through connectinglinks, later described in detail, movement of the operating member 20 isemployed to actuate a rocker post 24 that is fulcrumed intermediate itsends on a pivot member 25 carried by the support S adjacent its forwardend. Further as shown in Fig. 4, the rocker post 24 has a pivotalconnection 26 with the forward end of a horizontally disposed lever 27which extends rearwardly in parallel spaced relation with respect to thesupport plate S and which carries at its rear end a T-head 28 thatcooperates with a coupling disc 29 to rotate the disc in accordance withdirectional move-- ment of the lever 27. The disc is provided with upperand lower diametrically opposed lateral studs and 31, respectively,which are adapted to be received in a keeper slot 32 in the adjacentflange of the T-head. As indicated in Fig. 4, the upper stud 30 of thedisc 29 is engaged in the upper keeper slot on the T-head, so that whenthe rocker post 24 is actuated to shift the lever 27 rearwardly, to theright with respect to Fig. 4, a clock wise movement will be imparted tothe disc 29. This clockwise movement of the disc is transmitted througha depending L-shaped link 33 to the set of register pinions 21 wherebythe pinions are shifted from their neutral position intermediate therack bars down into mesh with the lower rack bars 23. The link 33 haspivotal connec' tion at its upper end with the disc 29 and is slidablewith shaft 34 which provides the mounting means for the freely rotatablepinions 21. It will be apparent that when the rocker post 24 isoppositely moved, the lever 27 will be pulled forwardly so that the disc29 is rocked in a counterclockwise direction. This movement of the disc20, acting through the link 33, will shift the register pinions upwardlyinto neutral position out of mesh with the lower rack bars. The lever 27is held with its T-head elevated in driving connection with the upperdisc studs 30 through the upward pull of a connector spring connectedbetween a stud 36 on the shank of the lever and a stud 37 carried by theinner end of a control lever 38 that is itself pivoted intermediate itsends as at 39 to a support element 4% for oscillation in a verticalplane. The forward end of the control lever has a terminal portion 41which, in the position of parts shown in Fig. 4, is held depressed by asubtract key element, not shown, of the machine in which the mechanismis incorporated. When the terminal 41 is freed, so that addition may beeffected, the lever 27 and its T-head 28 are permitted to drop down sothat the lower keeper slot 32 engages the lower disc stud 31, while theupper keeper slot 32 clears the stud 30. When thus positioned, it willbe apparent that rearward movement of the rocker post 24, driven fromits connecting linkage with the operating member 21), acts to rock thedisc 29 in a counterclockwise direction so that the register pinions areshifted from neutral position upwardly into engagement with the top bars22 of their racks. In like manner, but in reverse movement, when thepost 24 is rocked forwardly the lever 27 is pulled forwardly to rock thedisc 29 in a clockwise direction and thereby to lower the registerpinions out of mesh with their upper rack bars 22 and back into neutraldisengaged position.

It should here be pointed out that in the present disclosure the rackbars 22 and 23 comprise the upper and lower sides of separate racksarranged in denominational order for horizontal reciprocation forwardlyand rearwardly in coincidence with reciprocation of the operating member20. This arrangement is optional and is not by way of limitation. Whenthe racks go forward in the normal operation of entering items into themachine, the register pinions are shifted out of engagement with theirrespective rack bars and they remain out of engagement until theoperating member begins its rearward movement in the second half of itscycle. At this time the pinions are shifted into engagement with theirrack bars so that the operation of addition or subtraction as the casemay be is accomplished in the register. The pinions remain in mesh whenthe operating frame comes to its position of rest at its rear limit oftravel and are disengaged when the operating member next is cycled tobegin its forward movement. This is the normal operation of themechanism.

The linkage which constitutes the driving connection between theoperating member and the rocker post 24 is carried by the support platesS. As shown in Fig. 2. the operating member 20 has secured thereto aplate 42 to which is rigidly attached a double acting cam indicatedgenerally at 43. The structure of this cam is best shown in Figs. ll, 12and 13 in which it wil be seen that the body of the cam is substantiallyboatshaped and is positioned longitudinally of the path of reciprocation of the operating member 20. The cam is formed from a blockof material rectangular in crosssection that is relieved from its topface to provide downwardly inclined sloping faces that converge at themidpoint of the cam. The front end of the cam body has a nose portion 44provided with fOIW 9 vergent side faces 45, and at its rear end the cambody has a similar nose portion 46 provided with rearwardly convergentside faces 47. As shown in Figs. 11, 12 and 13, the convergent sidefaces of nose portions 44 and 46 intersect in the longtudinal axis ofthe cam body and this axis is in vertical registry with the longitudinalaxis of the support plate S. Directly behind the forward nose portion44, the downward sloping face of the cam body provides a riser 48 whichintersects with the rear riser portion 49 formed by the sloping faceextending up to the rear nose portion 46. This cam is adapted tocooperate with a pair of hell crank rockers 50 and 5'1, respectively,pivoted at the left hand side of the support plate S, and with a secondpair of bell crank rockers 52 and 53, respectively, pivoted at the righthand side of the support plate. The pivotal mounting for these rockerscomprises in each instance a pin 54 passed transversely through thesupport plate S to project at opposite sides thereof. The fulcrum pointof each bell crank rocker is apertured to play loosely over the pin, andan expansion spring 55 surrounding the shank of the pin betweencotter-key anchored washer 56 and a bearing washer 57 normally urges therocker laterally against the face of the support plate S. The fulcrumpoint aperture in each bell crank rocker is sufficiently large to permitlateral pivoting of the rocker on the pin and at the same time to permitfree pivoting movement of the rocker for oscillation in a verticalplane. Each bell crank rocker comprises a thin plate vertically disposedfor oscillation in a vertical plane parallel to the support plate S. Therocker 50 at the left hand side of the support plate is disposed overthe forward travel limit point of the operating member 20. The bottomedge of this rocker has a downwardly directed cam portion formed with anupwardly and forwardly inclined cam edge 58, and the body of the rockeris further provided at its bottom portion with a rearwardly directed lug59 that is flared laterally outward with respect to the vertical planeof the rocker to provide an inclined camming face adapted to cooperatewith the inclined face 45 of the forward nose of the cam 43 when theoperating member is moved to its forward limit position. The rocker 50also is provided at its front edge with a similar laterally andoutwardly inclined cam lug 60 that is directed forwardly for cooperationwith a cam element of displacement means, later described. The rear bellcrank rocker 51 is substantially similar to the rocker 50 and has aforwardly and downwardly inclined portion that provides a sloping camedge 61 which, when the operating member 20 is in its position of restat its rearward limit of travel, overrides the rear inclined riser 49 ofthe cam 43. The front edge of the rear rocker 51 is formed with aforwardly directed lug 62 that is flared forwardly and outwardly withrespect to the plane of the rocker. This lug 62 is adapted forcooperation with the displacement means, later described. The verticalextent of the lug 62 equals the combined vertical extent of the lugs 59and 60 on the forward rocker 50, so that the lower end portion of therear rocker lug 62 is adapted for cooperative camming engagement withthe adjacent inclined side face 47 of the rear nose 46 on the cam whenthe operating member 20 is moving rearwardly through the second half ofits cycle back into its limit position.

When the operating member 20, see Fig. 2, starts forward in the firsthalf of its cycle, its riser 49 cams against the overriding edge 61 ofthe bell crank rocker 51 and rocks the bell crank in a counterclockwisedirection. As the operating member continues forward, the bottom edge ofthe bell crank lever rides off the rear nose 46 of the cam 43. Rockingmovement of the bell crank 51 is transmitted through a pull link 63 tothe rocker post 24 to impart a forward rocking movement to the upper endportion of the rocker post. This link 63 parallels the support plate Sand is inclined forwardly and downwardly relative to the assembly. Atits rear end the link 63 has a pivotal connection 64 with a connectorlink 65 that is, in turn, pivoted at 66 to the upper portion of the bellcrank rocker 51. The connector link 65 has a forwardly directedextension that lies alongside the shank of the link 63 and which isprovided with a portion bent upon itself beneath the lower edge of thelink 63 to provide a keeper 67 which lies alongside the opposite side ofthe link 63. A contractile spring 68 ponnected between a point ofanchorage on the link 65 and a point of attachment on the link 63normally biases the link 63 downwardly into seated engagement in itskeeper 67. At its forward end the link 63 carries a hooked terminal 69that is adapted to engage over a lateral stud 70 carried by the lowerend of the rocker post 24. As the link 63 is pulled rearwardly bypivoting of the rocker 51, under the action of the cam on the operatingmember, the hook 69 engages the rocker post stud 70 to pull the lowerend of the rocker post rearwardly and thus correspondingly rock theupper portion of the post forwardly to impart a forward shift to thelever 27 for correspondingly rocking the disc 29, as previouslydescribed, to elevate the register pinions 21 out of mesh with the rackbars 23 for a shift to neutral disengaged position, as shown in Fig. 4.

As the operating member goes forward, the inclined face 45 of itsforward nose 44 engages behind the cam lug 59 of the forward rocker 50and cams the rocker plate laterally outward to accommodate passage ofthe cam 43. When the operating member reaches its forward limit oftravel the nose 44 of its cam will have passed beyond the lug 59 so thatthe rocker plate is permitted to shift back in the direction of thesupport plate to dispose its cam edge 58 in overriding relation to theforward riser 48 of the operating member cam. When the operating memberstarts rearwardly through the second half of its cycle it is necessarythat the register pinions be in engagement with their rack bars. As theoperating member starts back, its riser 48 earns the forward rocker 50to rock in a counterclockwise direction with respect to Fig. 2. Theupper end portion of the rocker 50 has a pivotal connection 71 with aconnector link 72, similar to the previously described connector link63, and which has pivotal connection 73 with the rear end of a pull link74. The connector link 72 also is formed with a keeper 75 which guidesthe link 74. A contractile spring 76 between a point of attachment onthe link 72 and a point of attachment on the link 74 biases the link 74into engagement against the bottom of its keeper. The forward end of thepull link 74 has a hooked terminal 77 adapted to engage over a lateralstud 78 carried by the rocker post 24 at a point above its fulcrum. Thepull of the linkage just described acts to rock the upper portion of therocker post 24 rearwardly, so that the lever 27, see Fig. 4, is shiftedrearwardly to effect a corresponding clockwise rotation of the disc 29,which acts to lower the register pinions 21 into engagement with theirrack bars. At this point it should be made clear that if the controllever 38 had been released to lower the lever 27 for engaging the lowerdisc stud 31 in the lower keeper slot 32, the shifting of the lever 27would have effected a counterclockwise rotation of the disc 29 whichwould have carried the pinions into mesh with the upper bars 22 of theirracks.

The rocker post 24 carries at its upper end a laterally disposed roller79 that is adapted to ride into either of two valleys 80 and 81 formedat the sides of a depending ridge member 82 in the bottom edge of adetent lever 83 that is pivoted at its rear end 84 to the support plateS. The forward end of the detent lever is biased downwardly by acontractile spring 85 connected between the end of the lever and a pointof attachment on the support plate. The bias of the detent lever 83serves to hold the rocker in either of the two positions to which it isshifted by the action of the linkage just described. As shown in Fig.15, the upper end of the rocker post 24 is adapted to contact limitingstop flanges 86 and 87, respectively, which are integral with ahorizontal plate 88. The plate 88 is secured to the support plate S sothat the flanges 86 and 87 depend in parallel spaced relation to definethe extent of rocking movement of the rocker post. The stop flanges holdthe rocker post on the sloping side of the detent ridge 82 before ittravels completely into the adjacent valley 80 or 81, so that it willnot override the throw of the lever 27 and cause jamming of the disclugs 30 and 31 relative to the head of the lever.

The linkage at the right hand side of the support plate S is illustratedin Fig. 1. This linkage is substantially similar to that at the lefthand side of the plate and comprises a connector link 89 pivotallyconnected as at 90 to the upper portion of the rear bell crank rocker53, with a pivotal connection 91 to the rear end of a horizontallydisposed pull link 92 that has a hooked terminal 93 at its forward endfor engagement over the upper stud 78 on the rocker post 24. Theconnector link 89 is provided with a keeper 94 and a spring 95 similarto the link 65, keeper 67, and spring 68 previously described. Thespring 95 biases the link 92 against the bottom of its keeper 94 toretain the linkage in proper assembly. The rear bell crank rocker 53 isidentical in structure to the rear rocker 51 at the left hand side ofthe assembly, except that its camming lug 96 is flared oppositelyoutward with respect to the plane of the rocker. In like manner theforward rocker 52 at the right hand side of the support plate isprovided with lugs 97 and 98 similar to the lugs 60 and 59 of theforward rocker at the left hand side of the assembly. These lugs havethe same function as those of the left hand forward rocker and areoppositely flared with respect to those at the left side. The upperportion of the rocker 53 has a pivotal connection 99 with the rear endof a pull link 100 which has attached to its forward end a hook terminal101 that is adapted to engage over the bottom stud 70 of the rocker post24. When the operating member 20 goes forward, and on its returnmovement, neither rocker 52 nor 53 is actuated during the normaladdition or subtraction operation of the register. The rockers 52 and 53normally are held laterally out of the path of movement of the cam 43 onthe operating member, as shown in Fig. 11. The rear rocker 53 is held inits outward position by the action of a displacement lever 102 that ispivoted intermediate its ends on a fulcrum 103 mounted in the supportplate S. At its upper end the lever 102 has connection with acontractile spring 104 that is anchored to a point of attachment on thesupport plate S to bias the upper end of the lever forwardly in theposition shown in Fig. 1. In this position a laterally and outwardlydirected cam 105 on the lower end of the lever is engaged against theside of the rocker to hold the rocker angled outwardly in the positionshown in Fig. 11. In this position the plate of the rocker is pivotedlaterally on the mounting pin 54 against the bias of the spring 55, andthe lug 96 on the rocker is held out of the path of travel of the cam onthe operating member. Also, due to the angled position of the rocker,its inclined bottom edge will be held out of position with respect tothe rear riser 49 on the cam of the operating member. Fig. 8 illustratesthat the cam 105 is an outwardly directed portion that extends at aright angle from the plane of lever 102 and is provided with arearwardly and inwardly inclined entrant edge 106, thus constituting thecam 105 substantially as a wedge member that is adapted to enter betweenthe support plate and the flared lug 96 of the rocker when thedisplacement lever 102 pivots to bring the cam 105 into engagement withthe rocker. When the displacement lever 102 is rocked to move the cam105 forwardly, by means later described, the cam moves out from behindthe rocker plate so that the rocker plate returns under the bias of thespring 55 against the support plate to the position as shown in Figs. 12and 13. In this position its lug 96 and lower cam edge override the pathof movement of the cam 43 on the operating member.

In like manner the forward rocker 52 is normally held out of the path ofmovement of the cam on the operating member by a second displacementlever 107 that is pivoted intermediate its ends to a fulcrum 108 mountedon the support plate S. The upper end of the lever 107 is biasedforwardly by a contractile spring 109 connected between the end of thelever and a point of attachment on an element of the frame of themachine on which the apparatus is incorporated. The lever 107 also isprovided at its lower end with a wedge cam 110 identical to the cam 105on the lever 102. When the displacement lever 107 is rocked to theposition shown in Fig. 1, its wedge cam 110 enters behind the rocker lug97 and forces it laterally outward from the support plate into theposition shown in Fig. 11, where both the rocker and its lug 98 are heldout of the path of movement of the cam on the operating member. Byreason of the holding action of the displacement levers 102 and 107,neither rocker 52 nor 53 can be actuated during the normal addition orsubtraction operation of the register.

At the left hand side of the support plate a second pair of displacementlevers functions similarly to the displacement levers on the right handside for the purpose of moving the bell crank rockers 50 and 51 out ofthe path of movement of the cam on the operating member. A displacementlever 111 is pivoted at the left hand side of the support plate on thefulcrum element 108. At its lower end the lever 111 is provided with awedge cam 112 that is identical to the wedge cam 105 of its companionlever at the right hand side, except that it is angled oppositely to thecam 105. A second displacement lever 113 is pivoted on the fulcrum 103and carries at its lower end a wedge cam 114 that is identical with thecam 112 on the forward displacement lever. in the normal operatingposition of the parts, as shown in Figs. 1 and 2, the wedge cams 112 and114 and their respective displacement levers are not engaged with therockers and thus do not hold them out of the path of movement of the camon the operating member. The lever 113 is biased into this non-engagedposition by means of a contractile spring 115 connected between theupper end of the lever and a point of attachment on the support plate S.A link 116 has a pivotal connection 117 at its rear end with the upperend of the displacement lever 113, and has also a pivotal connection 118with the upper end of the forward displacement lever 111. The bias ofspring 115 thus serves to hold both displacement levers in forwardposition with their wedge cams out of engagement with the rockers 50 and51. The lever 116 extends forwardly and is provided at its end with alaterally directed stud 119 that is adapted to cooperate with means,later described, for imparting horizontal shifting movement to the leverfor rocking the displacement levers 111 and 113. When the lever 116 ispulled forwardly, to the right with respect to Fig. 2, the displacementlevers 111 and 113 are correspondingly rocked to move their lower endsrearwardly and thus to carry the wedge cams 112 and 114 rearwardly toforce the rockers 50 and 51 outwardly out of the path of movement of thecam on the operating member in the position shown in Figs. 12 and 13.When thus conditioned, the cam 43 on the operating member 20 will haveno effect on the linkage at the left hand side of the support plate whenthe operating member is cycled.

The forward end of the support plate S has secured thereto a verticallydisposed stop plate 120 which extends transversely at opposite sides ofthe support plate, as shown in Fig. 6, for a sufficient verticaldistance to provide a stop for the forward ends of the links 92 and 100at the right hand side of the support plate and for the links 63 and 74at the left hand side. The stop plate 120 also provides a point ofanchorage for a contractile spring 121 attached to the forward endportion of the link 92, and for a contractile spring 122 attached to theforward end portion of the link 100 at the right hand side of thesupport plate. In like manner, on the left hand side of the supportplate, the stop 120 provides anchorage for a contractile spring 123 thatis connected to the forward end portion of the link 63 and for a contractile spring 124 that is connected to the forward end portion of thelink 74-. These springs serve to bias the links forwardly intoengagement against the stop plate 120 when they are not actively engagedwith the studs of the rocker post 24. This bias of the springs serves toposition the linkage so that the rockers 50, 51, 52 and 53 are held intheir proper positions for cooperation with the cam on the operatingmember. These springs serve also to pull their respective links andconnected bell crank rockers back to normal position at all times exceptwhen being acted upon by the cam on the operating member. The connectorlinks 65, 72 and 89 provide flexibility of coupling between therespective bell crank rockers and pull links, so that if the rocker 24were held against rocking under the pull of the links for any reason,the bell crank rockers still would be permitted to rock under theinfluence of the cam on the operating member without damaging the links.In such case, the rearward throw of the pivots 90, 66 and 71 wouldmerely pull the connector links rearwardly against the bias of theirrespective springs 95, 68 and 76 to pivot on the ends of theirassociated links without imparting any force greater than the tension oftheir respective springs.

When the mechanism is conditioned for the performance of a subtotaloperation it is necessary that the register pinions remain in mesh withtheir racks as the rack'! go forward and that they be held in meshduring the return stroke of the racks so that the amount taken from theregister in effecting the subtotal is restored to the register on returnof the racks. This necessitates a disposition of bell crank rockers asshown in Fig. 12, in which the rockers 50 and 51 at the left hand sideof the support plate S are displaced out of the path of movement of thecam on the operating member, while at the same time the forward rocker52 at the right hand side of the support plate is likewise displaced.The rocker 53 at the right hand side remains in position for actuationby the cam on the operating member. By virtue of this arrangement, whenthe operating member 20 goes forward it actuates only the rocker 53.This rocker, acting through the linkage previously described, throws theregister pinions into mesh with their respective racks. The racks movein accordance with the movement of the operating member. When theoperating member reaches its forward position the register pinionsremain in engagement with their racks because the forward bell crankrockers are held out of the path of movement of the cam 43. When theracks return with the return movement of the operating member travellingback in the second half of its cycle, the register pinions remain inengagement with their racks.

The mechanism for effecting the subtotal operation 18 best shown inFigs. 8, 9, l0 and 3. The rod 125 from the subtotal key of the machinein which the mechanism is incorporated extends rearwardly into the zoneof the timing mechanism, with its rear end supported for reciprocationin elements 126 and 127 of the machine frame. The subtotal rod has acollar 128 secured thereon by a set screw 129. When the subtotal key isactuated the rod 125 is moved rearwardly to carry with it the abuttingdepending end portion 130 of a horizontal arm 131 that is coupled with aparallel horizontal lever 132 in the manner shown in Fig. 14. The spacedparallel ends of the levers 131 and 132 are provided with pins 133 whichare seated in sockets in the ends of a sleeve 134 that is freelyrotatable on a depending stud shaft 135 that has threaded stemattachment 136 at its upper end with a support member 137 forming a partof the machine frame. A headed bolt 138 passed through the end of thelower lever 131 has threaded attachment in a receiving socket in the endof the shaft 135 to retain the lever against the end of the sleeve 134.A spacer sleeve 139 between the upper lever 132 and the support 137disposes the connection at the proper point for cooperation with otherelements of the mechanism. By reason of the coupling sleeve 134 it isevident that the levers 131 and 132 are connected for movement inunison. Rearward travel of the subtotal rod acting through the collar128 serves to rock the assembly of levers 131 and 132 on the fulcrumprovided by the shaft 135 so that the other end of the lever 132 ismoved forwardly. The end of the lever 132 carries an upstanding stud 140that engages behind the stud 119 on the link 116 which couples the upperends of the two displacement levers at the left hand side of the supportplate. As the end of the lever 132 is rocked forwardly the stud 119 iscarried forward to impart a forward pull to the lever 116 and thereby torock the displacement levers 111 and 113 to carry their respective wedgecams 112 and 114 into position behind the bell crank rockers 5t) and 51,so that these rockers are held out of the path of movement of the cam onthe operating member. At the same time, the rocking movement of thelever 132 is transmitted through a link 141 to free the cam wedge of thedisplacement lever 102 from the rear bell crank rocker 53 at the righthand side of the support plate so that the rocker moves into the path oftravel of the cam on the operating member. The link 141 extendsdiagonally rearwardly and downwardly with respect to the assembly and atits upper forward end it is provided with a horizontally directed lug142 that has a pivotal connection 143 with the end of the lever 132.Adjacent its lower end, the link 141 has a pivotal connection 144 withthe lower end portion of the displacement lever 102, so that forwardmovement of the link 141 under actuation by the lever 132 serves to rockthe lower end of the displacement lever 102 forwardly and release itswedge cam 195 from engagement with its associated bell crank rocker 53.

When the mechanism is to be conditioned for total taking operation, itis necessary that the same operations for subtotaling be carried outexcept that when the racks begin their return stroke the registerpinions require to be disengaged from their racks. This requires thatthe parts be disposed as shown in Fig. 13, with the forward bell crankrocker S2 at the right hand side of the support plate disposed in thepath of movement of the cam on the operating member. This disposition ofparts is effected by a joint movement of the rod 145 from the total keyof the machine and the subtotal rod 125. As shown in Fig. 10, the rod145 from the total key has end contact with a set screw-anchored collar146 on the subtotal rod 125, so that when the total rod 145 is movedrearwardly under actuation of its key, it carries with it the subtotalrod to accomplish the disposition of the linkage at the left hand sideof the support plate in the manner previously described. Forwardly ofits point of anchorage with the collar 146 the total rod 145 hasanchored thereon a collar 147 that abuts the tip of a short lever 148that is disposed alongside the forward end portion of a longitudinalshift bar 149. The short lever 148 has a pivotal connection 150 with theend of the bar 149 and is provided with a fixed stud 151 in engagementwith an edge portion of the shift bar. A contractile spring 152connected between the stud 151 and a stud 153 carried by the end of thebar 149 provides a connection between the bar and the short lever 148 sothat when the tip of the lever 148 is moved rearwardly upon actuation ofthe total key in the machine, the pull of the spring 152 acts to shiftthe bar 149 rearwardly. The spring 152 has sufficient tension toaccomplish this movement but is capable of yielding in the event ofjamming or holding any of the parts so that damage or breakage isavoided.

A contractile spring 154 between a point of attachment on a supportelement of the machine frame and a point of attachment on the bar 149serves to bias the bar to move forwardly so that its connected shortlever 148 is held in contact with the collar 147 on the total rod. Thisspring serves also to return the bar to normal position, as shown inFig. 10, when released. The bar 149 shifts horizontally on the frameelement 126. At its forward end it is provided with a closed end slot155 which plays over a guide stud 156 anchored to the frame, and at itsrear end the bar has a longitudinal end opening slot 157 that is guidedover a transverse shaft 158 that extends through the frame 126 to abearing support in the support plate S. The slot 157 and the bearing inthe support plate S journal the shaft 158 for oscillation. The end ofthe shaft 158 outwardly of the bar 149 has rigidly secured thereto acollar 159 to which is fixedly attached a finger 160 having a terminalportion disposed in the path of travel of a cam element 161 fixed to thebar 149. At its opposite end adjacent the support plate S as shown inFigure 7 the shaft 158 has fixedly secured thereto a cam element 162normally engaged over the upper edge of a link 163 which is adapted tocouple the displacement levers 102 and 107 for movement in unison. Therear end of the link 163 has a pivotal connection 164 with the upper endof the rear displacement lever 102 and adjacent its forward end the linkis formed with a hook 165 adapted for engagement over a lateral stud 166secured to the adjacent upper portion of the forward displacement lever107. A biasing spring 167 between a point of attachment on the rear endportion of the link 163 and a point of attachment on the upper end ofthe rear displacement lever 102 normally biases the link 163 upwardly sothat the hook 165 clears the displacement lever stud 166 when the reardisplacement lever 102 is rocked to move its upper end rearwardly. Inthis normal position of the parts the upper edge of the link 163 is inengagement with the cam 162, as shown in Fig. 7. When the total rod 145is moved rearwardly the bar 149 is correspondingly shifted to carry itscam 161 into engagement with the finger 160 and this action cams downthe finger 160 to effect a corresponding rotation of the shaft 158clockwise With respect to Figs. 10 and 7. As shown in Fig. 7, thisclockwise rotation of the shaft 158 carries down its cam 162 to depressthe link 163 and carry its hook 165 into a position where it will engagethe stud 166 on the forward displacement lever 107 when the reardisplacement lever 102 is rocked to exert a pull on the link.Consequently, when the link 141, Fig. 3, is pulled forwardly by theaction of the lever 132, as previously described, the rocking movementimparted to the rear displacement lever 102 is similarly imparted to theforward displacement lever 107, so that both displacement levers move inunison to withdraw their respective wedge cams from the bell crankrockers 52 and 53. This action permits these bell crank rockers at theright hand side of the support plate S to move under the bias of theirsprings 55 into the path of travel of the cam on the operating member.

Thus it will be seen that when the total rod 145 is actuated from itskey, mechanism is brought into operation, as described, to eifect acoupling of the upper ends of the displacement levers at the right handside of the support plate S, and this coupling is normally ineffectiveunder all other conditions. It is within the purview of this inventionthat a similar coupling arrangement may be provided for the twodisplacement levers at the left hand side of the support plate S. Suchan arrangement makes possible an independent operation of the left handdisplacement levers so that the parts can be conditioned for a non-addoperation of the racks and operating member. All that is necessary insuch case is to remove all bell crank rockers except that at the rearleft hand side from the path of travel of the cam on the operatingmember. It is the bell crank rocker at the rear on the left hand side ofthe support plate which controls the shifting of the register pinions tocarry them out of engagement with their racks at the start of forwardmovement of the operating member and the racks.

The above description is directed to a specific embodiment of theprinciples of this invention. The principles may be incorporated invarious other physical expressions and it is to be understood that theinvention is not limited to the details of the present disclosure. Broadaspects of the invention include a combination in which the operatingmember is movable between two limit positions and has associated with ita plurality of devices, such as actuators or the like, that are adaptedfor driven movement by the operating member to accomplish shifting ofthe register pinions into and from mesh with their respective racks. Theoperating member cooperates with a device located adjacent one limit ofits travel to shift the pinions in one direction, and it cooperates withanother device located adjacent the same limit position of its travelfor shifting the pinions in an opposite direction. At the other limit oftravel, the operating member cooperates with a device for shifting thepinions in one direction, and with another device located at the samelimit position for shifting the pinions in an opposite direction. Allthe devices are driven by a single fixed element of the operatingmember. Incorporated into this assembly is a selective control means bywhich the various devices are engaged with the driving element of theoperating member or disengaged therefrom selectively either singly or inany desired combination. A control means, not shown, operated to movelink 116 to the right with respect to Figure 2, would hold fromengagement all the devices so that the operating member may move througha cycle without effecting any shift of the register pinions.

Another broad principle of the invention involves a plurality oflinkages arranged so that one linkaged set operates in reverse to theother. These linkages are selectively controlled to establish a drivingconnection between the operating member and the pinion shiftingmechanism. When one linkage provides the connection the pinions areshifted in one direction and when another linkage provides theconnection they are shifted in an opposite direction. Modulating meanssuch as earn 162 shown in Figure 7 is employed in connection with thelinkages to alter their mode of operation under selective control toprovide various combinations of register shifting.

The invention also contemplates in its broad aspects a plurality ofselectively operative driving connections between the operating memberand the register shift mechanism. These connections are normallyconditioned to effect a shifting of the register pinions regardless ofthe position assumed by the pinions at any given instant in the cycle ofthe operating member. Means is provided for disabling any selectedconnection either wholly or in part so that the connection operatesthrough those parts not disabled. Another broad principle incorporatedin the invention deals with the moving parts of the mechanism. In thisinvention, when a register pinion shift is carried out, all thosemovable parts of the mechanism not ment of the cam. The actuators areadapted to be driven by the cam when the operating member is moving in acertain direction and when the cam clears any actuator the actuatorreturns to a position which normally would block return movement of thecam. The actuator is provided with cam means cooperative with the cam onits return movement to shift the actuator out of obstructing relation tothe cam for that interval necessary to permi the cam to continue itsmovement to the point of reengagement with the actuator. When this pointis reached the biasing means of the actuator returns it into operativengagement with the cam.

I claim:

1. In a calculating machine, a frame, an operating member movable in acycle between two limit positions, a cam on the operating member andmovable therewith in a predetermined path, a set of register pinionsadapted for shifting in opposite directions, two pairs of pinion shiftactuators on opposite sides of said path and mounted on said frame formovement individually into and out of said path, the actuators in eachpair being disposed adjacent opposite ends of said path, and meansselectively operative to dispose individual actuators in the path oftravel of the cam for actuation thereby and to remove the actuators fromsaid path of travel.

2. The structure of claim 1, and the actuators in each plaitr beingrelatively reversed as to the direction of pinion s i t.

3. The structure of claim 1, and the two pairs of actuators beingrelatively reversed as to the direction of pinion shift.

4. In a mechanism for shifting the register pinions in a calculatingmachine into and from rack mesh, a planar support, a pinion shiftactuator movable thereon, a reciprocable driving member, a cam on saidmember in the plane of the support, said actuator having a portionengageable with the cam from one side thereof when the cam is in atravel limit position to drive the actuator, means biasing the actuatorinto the path of travel of the cam, and a lateral deflector portion onthe actuator engageable by the cam when nearing a limit of its travel toshift the actuator laterally out of the path of cam travel until the camreaches that limit.

5. In a mechanism for shifting the register pinions in a calculatingmachine into and from rack mesh, a planar support, a pair of pinionshift actuators movable thereon in spaced relation at one side thereof,a pair of pinion shift actuators movable thereon in spaced relation atthe other side thereof, a reciprocable driving member engageable withsaid actuators in the plane of said support,

an individual displacement lever pivoted on the support adjacent eachactuator, and a cam on each lever engageable with its associatedactuator to prevent engagement with said driving member.

6. In a calculating machine having a pinion shiftable selectively intomeshing engagement with racks, an operating member movable between twopositions of adjustment during a cycle of operation, an actuating cammovable with the operating member, a plurality of actuation meansseparately movable and said means independently shiftable relative eachother into and out of the path of said actuating cam, an operativeconnection between each of said actuating means and said pinion foreifecting adjustment thereof responsive to operative engagement betweensaid actuating means and said cam, means enabling movement of the pinionby any one of the actuating means independently of movement to any otherof the plurality of said actuating means.

7. In a calculating machine having a pinion shiftable selectively intoand out of meshing engagement with racks, a rocker arm pivotedintermediate its ends, an operative connection between said rocker armand said pinion for causing shifting movement thereof responsive torocking movement of the arm between two positions of adjustment, anoperating member movable between two positions of adjustment during acycle of operation, an operative cam movable with the operating member,a plurality of actuator means separately mounted for swinging movementin a place into and out of the path of the cam and for rocking movementin another plane responsive to operative engagement with said cam, anoperative connection between said actuator means and said rocker arm foreffecting rocking movement thereof in response to operative engagementbetween any one of the said actuator means and said cam, and meansenabling rocking movement of the rocker arm independent of movement ofany other said actuator means.

8. In a calculating machine as claimed in claim 7 in which the operativeconnection between said actuator means and the rocker arm compriseslinkages pivoted at one end to the actuator means, and having a hookedportion at the other end, and posts extending from said rocker arm onopposite sides of the pivot and adapted to be operatively engaged by thehooked end portions of the linkages.

9. In a calculating machine as claimed in claim 8 in which the hookedend portion of each of the linkages comprises an elongate groove inwhich the posts may freely slide to permit lost motion whereby therocker arm may be shifted between its two positions of adjustmentindependently of the linkages and the actuator means associatedtherewith.

10. In combination in a machine of the type described, a fixed framemember, a shiftable set of register pinions, a shifting member mountedfor movement relatively to said frame member and connected with saidpinions to shift them by such movement, an operating member shiftablelinearly forward and back during a cycle of operation, a cam memberthereon, a plurality of actuators mounted on said frame memberindependently of said pinion shifting member for movement between normaland operated positions of adjustment and for movement into and out ofthe path of said cam, means biasing said actuator into normal positionin the path of said cam, means forming a part of said cam and saidactuator for causing shifting movement of said actuator from normalposition to operated position responsive to operative engagement withthe cam upon movement in one direction and for deflecting said actuatorin another direction out of the path of said cam upon operativeengagement during movement of the cam in the opposite direction, andindividual connecting means each connecting a respective one of saidactuators with said pinion shifting member and each comprising elementscoacting to move said shifting member to shift said pinions uponmovement of the respective actuator from said normal position to saidoperated position by said cam, to permit movement of said shiftingmember by any other of said actuators without movement of saidrespective actuator, and to permit said respective actuator to bedeflected out of the path of said cam without moving said pinionshifting member.

11. In a calculating machine, an operating member movable between twolimit positions in a cycle of operation, a set of register pinionsadapted for shifting movement in opposite directions, actuating means onsaid operating member and movable therewith in a predetermined path, twopairs of pinion shift actuators, said two pairs being on opposite sidesof said path and the two actuators of each pair being adjacent oppositeends of said path, said pinion shift actuators being mounted forshifting movement in one direction into and out of the path of movementof said actuating means and for shifting movement in a differentdirection from the first responsive to actuation by said actuatingmeans, means individually biasing all of said actuators into the path oftravel of said actuating means for engagement thereby, and meansoperative selectively to remove individual actuators from the path oftravel of said actuating means.

12. In a calculating machine, an operating member movable between twolimit positions in a cycle of operation, a set of register pinionsadapted for shifting movement in opposite directions, actuating means onsaid operating member and movable therewith in a predetermined path, twopairs of pinion shift actuators, said two pairs being on opposite sidesof said path and the two actuators of each pair being adjacent oppositeends of said path, said pinion shift actuators being shiftable in onedirection into and out of the path of movement of said actuating meansand shiftable from normal to operated position in another directionresponsive to actuation by said actuating means, means individuallybiasing each of said actuators into the path of travel of said actuatingmeans for operative engagement thereby, means operative selectively toremove said actuators from the path of travel of said actuating means,and means individually biasing each of said actuators from operated tonormal position upon disengagement by said actuating means.

l3. In a calculating machine of the type described, an operating membermovable in a cycle between two limit positions, a set of registerpinions adapted for shifting movement in opposite directions, actuatingmeans on the operating member shiftable therewith in a path of movement,a pair of pinion shift actuators positioned on each side of the path ofmovement of the operating member adjacent each of the limit positions,said pinion shift actuators being shiftable in one direction into andout of the path of movement of said actuating means and shiftable inanother direction from normal to operated position responsive toactuation by said actuating means, means individually biasing each ofsaid actuators into the path of travel of said actuating means forengagement thereby, and means operative selectively to remove saidactuators from the path of travel of said actuating means.

14. In a calculating machine of the type described, an operating membermovable in a cycle between two limit positions, a set of registerpinions adapted for shifting movement in opposite directions, actuatingmeans on the operating member shiftable therewith in a path of movement,a pair of pinion shift actuators positioned on each side of the path ofmovement of the operating member adjacent each of the limit positions,said pinion shift actuators being shiftable in one direction into andout of the path of movement of said actuating means and shiftable inanother direction from normal to operated position responsive toactuation by said actuating means, means individually biasing each ofsaid actuators into the path of travel of said actuating means forengagement thereby, means operative selectively to remove said actuatorsfrom the path of travel of said actuating means, and means individuallybiasing each of said actuators to return from operated position tonormal position upon its engagement by said actuating means.

15. In a calculating machine, an operating member movable in a cyclebetween two limit positions, a set of register pinions adapted forshifting movement in opposite directions, actuator means biased toposition to engage the operating member adjacent one limit position foractuation thereby to shift the pinions in one direction, other actuatormeans biased to position to engage the operating member adjacent itsother limit position for actuation thereby to shift the pinions in anopposite direction, said actuator means being movable from normal toactuated position upon engagement with said operating member foractuating shifting movement of the pinions, means coupled with saidactuator means for returning the actuator means to normal positionindependent of shifting movement of the pinions, and means operativeselectively to hold out of biased position any of said actuator meansindependently of each other.

16. In a calculating machine, an operating member movable in a cyclebetween two limit positions, a set of register pinions adapted forshifting movement in opposite directions, actuator means biased toengage the operating member adjacent one limit position for actuationthereby to shift the pinions in one direction, other actuator meansbiased to engage the operating member adjacent its other limit positionfor actuation thereby to shift the pinions in an opposite direction, andsimilar actuator means also adjacent the limit positions of theoperating member for actuation thereby to shift the pinions in a reversedirection relative the limit position of first said actuator means, andmeans whereby the movement of any of said actuator means by saidoperating member is effected independently of movement to any other ofsaid actuator means.

17. In a calculating machine, a supporting plate, an operating membermovable linearly forward and back in a cycle of operation, a cam havingtwo working sides operatively connected with said operating member formovement therewith, a set of register pinions adapted for shiftingmovement in opposite directions, pinion shift actuators on one side ofthe cam and other pinion shift actuators on the other side of the cam,means mounting said actuators on the supporting plate in a positionnormally to lie in the path of the cam, means operable by each actuatorfor shifting the pinions in one direction, means individually biasingeach of said actuators into the path of travel of said cam forengagement thereby to drive the actuators, and means on the plateoperative selectively to remove individual actuators from the path oftravel of the cam.

References Cited in the file of this patent UNITED STATES PATENTS1,118,682 Reed Nov. 24, 1914 1,934,747 Sundstrand Nov. 14, 19331,946,505 Sundstrand Feb. 13, 1934 1,957,501 Horton May 8, 19342,110,987 Kammel Mar. 15, 1938 2,194,270 Sundstrand Mar. 19, 19402,222,373 Rauh Nov. 19, 1940 2,226,960 Anderson Dec. 31, 1940 2,255,623Landsiedel Sept. 9, 1941 2,285,311 Sundstrand June 2, 1947

